Family of five-speed transmission mechanisms having three planetary gear sets and four clutches

ABSTRACT

The family of transmissions has a plurality of members that can be utilized in powertrains to provide at least five forward speed ratios and one reverse speed ratio. The transmission family members include three planetary gear sets and four clutches. The powertrain includes an engine and torque converter that is continuously connected to at least one member of the planetary gear arrangement and an output member that is continuously connected with another of the planetary gear members. At least one other planetary gear member is continuously connected with the transmission housing. The four clutches provide interconnections between various gear members and with the input and the output shaft, and are operated in combinations of two to establish at least five forward speed ratios.

BACKGROUND OF THE INVENTION

[0001] 1. Field of the Invention

[0002] The present invention relates to a family of power transmissionshaving three planetary gear sets that are controlled by four clutches toprovide at least five forward speed ratios and one reverse speed ratio.

[0003] 2. Background Art

[0004] Passenger vehicles include a powertrain that is comprised of anengine, multi-speed transmission, and a differential or final drive. Themulti-speed transmission increases the overall operating range of thevehicle by permitting the engine to operate through its torque range anumber of times. The number of forward speed ratios that are availablein the transmission determines the number of times the engine torquerange is repeated. Early automatic transmissions had two speed ranges.This severely limited the overall speed range of the vehicle andtherefore required a relatively large engine that could produce a widespeed and torque range. This resulted in the engine operating at aspecific fuel consumption point during cruising, other than the mostefficient point. Therefore, manually-shifted (countershafttransmissions) were the most popular.

[0005] With the advent of three- and four-speed automatic transmissions,the automatic shifting (planetary gear) transmission increased inpopularity with the motoring public. These transmissions improved theoperating performance and fuel economy of the vehicle. The increasednumber of speed ratios reduces the step size between ratios andtherefore improves the shift quality of the transmission by making theratio interchanges substantially imperceptible to the operator undernormal vehicle acceleration.

[0006] It has been suggested that the number of forward speed ratios beincreased to five and even six speeds. Five-speed transmissions aredisclosed in U.S. Pat. Nos. 5,879,264; 5,984,825; 5,997,429; 6,007,450;and 6,056,665 issued to Raghavan, Hebbale and Usoro on Mar. 9, 1999;Nov. 16, 1999; Dec. 7, 1999; Dec. 28, 1999 and May 2, 2000,respectively; and U.S. Pat. No. 5,951,432 issued to Wehking, Hebbale,Raghavan and Usoro on Sep. 14, 1999. Six-speed transmissions aredisclosed in U.S. Pat. No. 4,070,927 issued to Polak on Jan. 31, 1978;U.S. Pat. No. 6,071,208 issued to Koivunen on Jun. 6, 2000; U.S. Pat.No. 5,106,352 issued to Lepelletier on Apr. 21, 1992; and U.S. Pat. No.5,599,251 issued to Beim and McCarrick on Feb. 4, 1997.

[0007] Five-speed transmissions offer several advantages over four speedtransmissions, including improved vehicle acceleration and improved fueleconomy. While many trucks employ power transmissions, such as Polak,having six or more forward gear ratios, passenger cars are stillmanufactured with three- and four-speed automatic transmissions andrelatively few five or six-speed devices due to the size and complexityof these transmissions. The Raghavan, Hebbale, Usoro and Wehking patentsemploy two planetary gear sets, and five or six torque transmittingmechanisms to provide five forward speeds.

SUMMARY OF THE INVENTION

[0008] It is an object of the present invention to provide an improvedfamily of transmissions having three planetary gear sets controlled toprovide at least five forward speed ratios.

[0009] In one aspect of the present invention, the family oftransmissions has three planetary gear sets, each of which includes afirst, second and third member, which members may comprise a sun gear, aring gear, or a planet carrier assembly member.

[0010] In another aspect of the present invention, each of the planetarygear sets may be of the single pinion-type or of the double pinion-type.

[0011] In yet another aspect of the present invention, a firstinterconnecting member continuously interconnects the first member ofthe first planetary gear set with the first member of the secondplanetary gear set.

[0012] In still another aspect of the invention, a secondinterconnecting member continuously interconnects the second member ofthe second planetary gear set with the first member of the thirdplanetary gear set.

[0013] In another aspect of the invention, a transmission housing iscontinuously connected with a second member of the first planetary gearset.

[0014] In yet a further aspect of the invention, each family memberincorporates an input shaft which is continuously interconnected with amember of the first, second or third planetary gear sets, and an outputshaft which is continuously connected with another member of the first,second or third planetary gear sets.

[0015] In another aspect of the invention, a first clutch selectivelyinterconnects a member of the first planetary gear set with the inputshaft, the output shaft, the first or second interconnecting member or amember of the second or third planetary gear sets.

[0016] In still a further aspect of the invention, a second clutchselectively interconnects a member of the second planetary gear set withthe input shaft, the output shaft, or a member of the first or thirdplanetary gear sets.

[0017] In a still further aspect of the invention, a third clutchselectively interconnects a member of the third planetary gear set withthe input shaft, the output shaft, the first or second interconnectingmember, or a member of the first or second planetary gear set.

[0018] In a still further aspect of the invention, a fourth clutchselectively interconnects a member of the first, second, or thirdplanetary gear sets with another member of the first, second, or thirdplanetary gear sets.

[0019] In still another aspect of the invention, the four clutches areselectively engageable in combinations of two to yield at least fiveforward speed ratios and one reverse speed ratio.

[0020] The above objects and other objects, features, and advantages ofthe present invention are readily apparent from the following detaileddescription of the best modes for carrying out the invention when takenin connection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

[0021]FIG. 1a is a schematic representation of a powertrain including aplanetary transmission incorporating a family member of the presentinvention;

[0022]FIG. 1b is a truth table and chart of some of the operatingcharacteristics of the powertrain shown in FIG. 11a;

[0023]FIG. 2a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0024]FIG. 2b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 2a;

[0025]FIG. 3a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0026]FIG. 3b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 3a;

[0027]FIG. 4a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0028]FIG. 4b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 4a;

[0029]FIG. 4a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0030]FIG. 5b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 4a;

[0031]FIG. 6a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0032]FIG. 6b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 6a;

[0033]FIG. 7a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0034]FIG. 7b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 7a;

[0035]FIG. 8a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0036]FIG. 8b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 8a;

[0037]FIG. 9a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0038]FIG. 9b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 9a;

[0039]FIG. 10a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0040]FIG. 10b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 10a;

[0041]FIG. 11a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0042]FIG. 11b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 11a;

[0043]FIG. 12a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0044]FIG. 12b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 12a;

[0045]FIG. 13a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0046]FIG. 13b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 13a;

[0047]FIG. 14a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0048]FIG. 14b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 14a;

[0049]FIG. 15a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0050]FIG. 15b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 15a;

[0051]FIG. 16a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention; and

[0052]FIG. 16b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 16a.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0053] Referring to the drawings, wherein like characters represent thesame or corresponding parts throughout the several views, there is shownin FIG. 1a a powertrain 10 having a conventional engine and torqueconverter 12, a planetary transmission 14, and a conventional finaldrive mechanism 16.

[0054] The planetary transmission 14 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 18, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 18 includes three planetary gear sets 20, 30 and 40.

[0055] The planetary gear set 20 includes a sun gear member 22, a ringgear member 24, and a planet carrier assembly 26. The planet carrierassembly 26 includes a plurality of pinion gears 27 rotatably mounted ona carrier member 29 and disposed in meshing relationship with both thesun gear member 22 and the ring gear member 24.

[0056] The planetary gear set 30 includes a sun gear member 32, a ringgear member 34, and a planet carrier assembly member 36. The planetcarrier assembly member 36 includes a plurality of pinion gears 37rotatably mounted on a carrier member 39 and disposed in meshingrelationship with both the sun gear member 32 and the ring gear member34.

[0057] The planetary gear set 40 includes a sun gear member 42, a ringgear member 44, and a planet carrier assembly member 46. The planetcarrier assembly member 46 includes a plurality of pinion gears 47rotatably mounted on a carrier member 49 and disposed in meshingrelationship with both the sun gear member 42 and the ring gear member44.

[0058] The planetary gear arrangement 18 also includes four torquetransmitting mechanisms 50, 52, 54 and 56. The torque-transmittingmechanisms 50, 52, 54 and 56 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0059] The input shaft 17 is continuously connected with the sun gearmember 42, and the output shaft 19 is continuously connected with thesun gear member 32. The planet carrier assembly member 26 iscontinuously connected with the planet carrier assembly member 36through the interconnecting member 70. The ring gear member 34 iscontinuously connected with the ring gear member 44 through theinterconnecting member 72. The ring gear member 22 is continuouslyconnected with the transmission housing 60.

[0060] Sun gear member 42 is selectively connectable with the ring gearmember 24 through the clutch 50. The planet carrier assembly member 46is selectively connectable with the ring gear member 24 through theclutch 52. The planet carrier assembly member 36 is selectivelyconnectable with the ring gear member 34 through the clutch 54. Theplanet carrier assembly member 36 is selectively connectable with theplanet carrier assembly member 46 through the clutch 56.

[0061] As shown in FIG. 1b, and in particular the truth table disclosedtherein, the torque-transmitting mechanisms are selectively engaged incombinations of two to provide five forward speed ratios and a reversespeed ratio. It should also be noted in the truth table that thetorque-transmitting mechanism 52 remains engaged through a neutralcondition, thereby simplifying the forward/reverse interchange.

[0062] To establish the reverse speed ratio, the clutches 50 and 52 areengaged. The clutch 50 connects the ring gear member 24 to the sun gearmember 42, and the clutch 52 connects the ring gear member 24 to theplanet carrier assembly member 46. The sun gear member 22 does notrotate. The planet carrier assembly member 26 rotates at the same speedas the planet carrier assembly member 36. The sun gear member 24 rotatesat the same speed as the planet carrier assembly member 46, the sun gearmember 42, and the input shaft 17. The speed of the planet carrierassembly member 26 is determined from the speed of the ring gear member24, and the ring gear/sun gear tooth ratio of the planetary gear set 20.The ring gear member 34 rotates at the same speed as the ring gearmember 44. The sun gear member 32 rotates at the same speed as theoutput shaft 19. The planet carrier assembly member 36 rotates at aspeed determined by the speed of the ring gear member 34, the speed ofthe sun gear member 32, and the ring gear/sun gear tooth ratio of theplanetary gear set 30. The overall numerical value of the reverse speedratio is determined from the ring gear/sun gear tooth ratios of theplanetary gear sets 20 and 30.

[0063] The first forward speed ratio is established with the engagementof the clutches 52 and 54. Clutch 52 connects the ring gear member 24 tothe planet carrier assembly member 46, and the clutch 54 connects thering gear member 34 to the planet carrier assembly member 36. Sun gearmember 22 does not rotate. The ring gear member 24 rotates at the samespeed as the planet carrier assembly member 46. The planet carrierassembly member 26 rotates at the same speed as the planet carrierassembly member 36, and the ring gear members 34,44. The planet carrierassembly member 26 rotates at a speed determined by the speed of thering gear member 24 and the ring gear/sun gear tooth ratio of theplanetary gear set 20. The sun gear member 32 rotates at the same speedas the output shaft 19. The sun gear member 42 rotates at the same speedas the input shaft 17. The planet carrier assembly member 46 rotates ata speed determined by the speed of the ring gear member 44, the speed ofthe sun gear member 42, and the ring gear/sun gear tooth ratio of theplanetary gear set 40. The overall numerical value of the first forwardspeed ratio is determined from the tooth ratios of the planetary gearsets 20 and 40.

[0064] The second forward speed ratio is established with the engagementof the clutches 50 and 54. The clutch 50 connects the ring gear member24 to the sun gear member 42, and the clutch 54 connects the planetcarrier assembly member 36 to the ring gear member 34. The sun gearmember 22 does not rotate. The ring gear member 24 rotates at the samespeed as the sun gear member 42 and the input shaft 17. The planetcarrier assembly member 26 rotates at the same speed as the planetcarrier assembly member 36, and the ring gear members 34 and 44. Theplanet carrier assembly member 26 rotates at a speed determined by thespeed of the ring gear member 24 and the ring gear/sun gear tooth ratioof the planetary gear set 20. The overall numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 20.

[0065] The third forward speed ratio is established with the engagementof the clutches 54 and 56. In this configuration, the input shaft 17 isdirectly connected to the output shaft 19. The numerical value of thethird forward speed ratio is 1.

[0066] The fourth forward speed ratio is established with the engagementof the clutches 50 and 56. The clutch 50 connects the ring gear member24 to the sun gear member 42, and the clutch 56 connects the planetcarrier assembly member 36 to the planet carrier assembly member 46. Thesun gear member 22 does not rotate. The ring gear member 24 rotates atthe same speed as the sun gear member 42 and the input shaft 17. Theplanet carrier assembly member 26 rotates at the same speed as theplanet carrier assembly members 36 and 46. The planet carrier assemblymember 26 rotates at a speed determined by the speed of the ring gearmember 24 and the ring gear/sun gear tooth ratio of the planetary gearset 20. The ring gear member 34 rotates at the same speed as the ringgear member 44. The sun gear member 32 rotates at the same speed as theoutput shaft 19. The planet carrier assembly member 36 rotates at aspeed determined by the speed of the ring gear member 34, the speed ofthe sun gear member 32, and the ring gear/sun gear tooth ratio of theplanetary gear set 30. The planet carrier assembly member 46 rotates ata speed determined by the speed of the ring gear member 44, the speed ofthe sun gear member 42, and the ring gear/sun gear tooth ratio of theplanetary gear set 40. The overall numerical value of the fourth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 20, 30 and 40.

[0067] The fifth forward speed ratio is established with the engagementof the clutches 52 and 56. The clutch 52 connects the ring gear member24 to the planet carrier assembly member 46, and the clutch 56 connectsthe planet carrier assembly member 36 to the planet carrier assemblymember 46. The sun gear member 22 does not rotate. The ring gear member24 rotates at the same speed as the planet carrier assembly members 26,36 and 46. The ring gear members 34 and 44 rotate at the same speed. Thesun gear member 32 rotates at the same speed as the output shaft 19. Thespeed of the planet carrier assembly member 36 is determined from thespeed of the ring gear member 34, the speed of the sun gear member 32,and the ring gear/sun gear tooth ratio of the planetary gear set 30. Thesun gear member 42 rotates at the same speed as the input shaft 17. Theplanet carrier assembly member 46 rotates at a speed determined by thespeed of the ring gear member 44, the speed of the sun gear member 42,and the ring gear/sun gear tooth ratio of the planetary gear set 40. Theoverall numerical value of the fifth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets30 and 40.

[0068] As set forth above, the engagement schedules for thetorque-transmitting mechanisms are shown in the truth table of FIG. 1b.This truth table also provides an example of speed ratios that areavailable utilizing the ring gear/sun gear tooth ratios given by way ofexample in FIG. 1b. The R1/S1 value is the tooth ratio of the planetarygear set 20; the R2/S2 value is the tooth ratio of the planetary gearset 30; and the R3/S3 value is the tooth ratio of the planetary gear set40. Also, the chart of FIG. 1b describes the ratio steps that areattained utilizing the sample of tooth ratios given. For example, thestep ratio between the first and second forward ratios is 1.65, whilethe step ratio between the reverse and first forward ratio is −0.67. Itcan also be readily determined from the truth table of FIG. 1b that allof the single step forward ratio interchanges are of the singletransition variety, as are the double step forward ratio interchanges.

[0069]FIG. 2a shows a powertrain 110 having a conventional engine andtorque converter 12, a planetary transmission 114, and a conventionalfinal drive mechanism 16.

[0070] The planetary transmission 114 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 118, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 118 includes three planetary gear sets 120, 130 and 140.

[0071] The planetary gear set 120 includes a sun gear member 122, a ringgear member 124, and a planet carrier assembly 126. The planet carrierassembly 126 includes a plurality of pinion gears 127 rotatably mountedon a carrier member 129 and disposed in meshing relationship with boththe sun gear member 122 and the ring gear member 124.

[0072] The planetary gear set 130 includes a sun gear member 132, a ringgear member 134, and a planet carrier assembly member 136. The planetcarrier assembly member 136 includes a plurality of pinion gears 137rotatably mounted on a carrier member 139 and disposed in meshingrelationship with both the sun gear member 132 and the ring gear member134.

[0073] The planetary gear set 140 includes a sun gear member 142, a ringgear member 144, and a planet carrier assembly member 146. The planetcarrier assembly member 146 includes a plurality of pinion gears 147rotatably mounted on a carrier member 149 and disposed in meshingrelationship with both the sun gear member 142 and the ring gear member144.

[0074] The planetary gear arrangement 118 also includes four torquetransmitting mechanisms 150, 152, 154 and 156. The torque-transmittingmechanisms 150, 152, 154 and 156 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0075] The input shaft 17 is continuously connected with the ring gearmember 144, and the output shaft 19 is continuously connected with theplanet carrier assembly member 146. The planet carrier assembly member126 is continuously connected with the planet carrier assembly member136 through the interconnecting member 170. The ring gear member 134 iscontinuously connected with the planet carrier assembly member 146through the interconnecting member 172. The ring gear member 124 iscontinuously connected with the transmission housing 160.

[0076] The sun gear member 122 is selectively connectable with the sungear member 132 through the clutch 150. The sun gear member 122 isselectively connectable with the sun gear member 142 through the clutch152. The planet carrier assembly member 136 is selectively connectablewith the ring gear member 142 through the clutch 154. The planet carrierassembly member 126 is selectively connectable with the ring gear member144 through the clutch 156.

[0077] The truth table of FIG. 2b describes the engagement sequenceutilized to provide five forward speed ratios and a reverse speed ratioin the planetary gear arrangement 118 shown in FIG. 2a.

[0078] To establish the reverse speed ratio, the clutches 150 and 156are engaged. The clutch 150 connects the sun gear member 122 to the sungear member 132, and the clutch 156 connects the planet carrier assemblymember 126 to the ring gear member 144. The ring gear member 124 doesnot rotate. The sun gear members 122 and 132 rotate at the same speed.The planet carrier assembly member 126 rotates at the same speed as theplanet carrier assembly member 136, the ring gear member 144, and theinput shaft 17. The sun gear member 122 rotates at a speed determined bythe speed of the planet carrier assembly member 126 and the ringgear/sun gear tooth ratio of the planetary gear set 120. The ring gearmember 134 rotates at the same speed as the planet carrier assemblymember 146 and the output shaft 19. The ring gear member 134 rotates ata speed determined by the speed of the planet carrier assembly member136, the speed of the sun gear member 132, and the ring gear/sun geartooth ratio of the planetary gear set 130. The overall numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 120 and 130.

[0079] The first forward speed ratio is established with the engagementof the clutches 150 and 152. The clutch 150 connects the sun gear member122 to the sun gear member 132, and the clutch 152 connects the sun gearmember 122 to the sun gear member 142. The ring gear member 124 does notrotate. The sun gear member 122 rotates at the same speed as the sungear members 132 and 142. The planet carrier assembly member 126 rotatesat the same speed as the planet carrier assembly member 136. The planetcarrier assembly member 126 rotates at a speed determined by the speedof the sun gear member 122 and the ring gear/sun gear tooth ratio of theplanetary gear set 120. The ring gear member 134 rotates at the samespeed as the planet carrier assembly member 146 and the output shaft 19.The planet carrier assembly member 136 rotates at a speed determined bythe speed of the ring gear member 134, the speed of the sun gear member132, and the ring gear/sun gear tooth ratio of the planetary gear set130. The ring gear member 144 rotates at the same speed as the inputshaft 17. The planet carrier assembly member 146 rotates at a speeddetermined by the speed of the ring gear member 144, the speed of thesun gear member 142, and the ring gear/sun gear tooth ratio of theplanetary gear set 140. The overall numerical value of the first forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 120, 130 and 140.

[0080] The second forward speed ratio is established with the engagementof the clutches 150 and 154. The clutch 150 connects the sun gear member122 to the sun gear member 132, and the clutch 154 connects the planetcarrier assembly member 136 to the sun gear member 142. The ring gearmember 124 does not rotate. The sun gear member 122 rotates at the samespeed as the sun gear member 132. The planet carrier assembly member 126rotates at the same speed as the planet carrier assembly member 136 andthe sun gear member 142. The planet carrier assembly member 126 rotatesat a speed determined by the speed of the sun gear member 122 and thering gear/sun gear tooth ratio of the planetary gear set 120. The ringgear member 134 rotates at the same speed as the planet carrier assemblymember 146 and the output shaft 19. The planet carrier assembly member136 rotates at a speed determined by the speed of the ring gear member134, the speed of the sun gear member 132, and the ring gear/sun geartooth ratio of the planetary gear set 130. The ring gear member 144rotates at the same speed as the input shaft 17. The planet carrierassembly member 146 rotates at a speed determined by the speed of thering gear member 144, the speed of the sun gear member 142, and the ringgear/sun gear tooth ratio of the planetary gear set 140. The overallnumerical value of the second forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets120, 130 and 140.

[0081] The third forward speed ratio is established with the engagementof the clutches 152 and 154. The clutch 152 connects the sun gear member122 to the sun gear member 142, and the clutch 154 connects the planetcarrier assembly member 136 to the sun gear member 142. The ring gearmember 124 does not rotate. The planet carrier assembly member 126rotates at the same speed as the planet carrier assembly member 136, thesun gear member 142, and the sun gear member 122. The ring gear member134 rotates at the same speed as the planet carrier assembly member 146and the output shaft 19. The ring gear member 144 rotates at the samespeed as the input shaft 17. The speed of the planet carrier assemblymember 146, and therefore the output shaft speed, is determined from thespeed of the ring gear member 144, the speed of the sun gear member 142,and the ring gear/sun gear tooth ratio of the planetary gear set 140.The overall numerical value of the third forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 140.

[0082] The fourth forward speed ratio is established with the engagementof the clutches 154 and 156. In this configuration, the input shaft 17is directly connected to the output shaft 19. The numerical value of thefourth forward speed ratio is 1.

[0083] The fifth forward speed ratio is established with the engagementof the clutches 152 and 156. The clutch 152 connects the sun gear member122 to the sun gear member 142. The clutch 156 connects the planetcarrier assembly member 126 to the ring gear member 144. The ring gearmember 124 does not rotate. The sun gear member 122 rotates at the samespeed as the sun gear member 142. The planet carrier assembly member 126rotates at the same speed as the planet carrier assembly member 136, thering gear member 144, and the input shaft 17. The sun gear member 122rotates at a speed determined by the speed of the planet carrierassembly member 126 and the ring gear/sun gear tooth ratio of theplanetary gear set 120. The ring gear member 134 rotates at the samespeed as the planet carrier assembly member 146 and the output shaft 19.The planet carrier assembly member 146 rotates at a speed determined bythe speed of the ring gear member 144, the speed of the sun gear member142, and the ring gear/sun gear tooth ratio of the planetary gear set140. The overall numerical value of the fifth forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 120 and 140.

[0084] As set forth above, the truth table of FIG. 2b describes theengagement sequence of the torque transmitting mechanisms utilized toprovide a reverse drive ratio and five forward speed ratios. It can bereadily determined from the truth table that all the single step forwardinterchanges are of the single transition type, as are the double stepforward interchanges. The truth table also provides an example of theratios that can be attained with the family members shown in FIG. 2autilizing the sample tooth ratios given in FIG. 2b. The R1/S1 value isthe tooth ratio of the planetary gear set 120; the R2/S2 value is thetooth ratio of the planetary gear set 130; and the R3/S3 value is thetooth ratio of the planetary gear set 140. Also shown in FIG. 2b are theratio steps between single step ratios in the forward direction as wellas the reverse to first ratio step. For example, the first to secondstep ratio is 1.8.

[0085] Turning to FIG. 3a, a powertrain 210 includes the engine andtorque converter 12, a planetary transmission 214, and a final drivemechanism 16. The planetary transmission 214 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 218, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 218 includes three planetary gear sets 220, 230 and 240.

[0086] The planetary gear set 220 includes a sun gear member 222, a ringgear member 224, and a planet carrier assembly 226. The planet carrierassembly 226 includes a plurality of pinion gears 227 rotatably mountedon a 15 carrier member 229 and disposed in meshing relationship withboth the sun gear member 222 and the ring gear member 224.

[0087] The planetary gear set 230 includes a sun gear member 232, a ringgear member 234, and a planet carrier assembly member 236. The planetcarrier assembly member 236 includes a plurality of pinion gears 237rotatably mounted on a carrier member 239 and disposed in meshingrelationship with both the sun gear member 232 and the ring gear member234.

[0088] The planetary gear set 240 includes a sun gear member 242, a ringgear member 244, and a planet carrier assembly member 246. The planetcarrier assembly member 246 includes a plurality of pinion gears 247rotatably mounted on a carrier member 249 and disposed in meshingrelationship with both the sun gear member 242 and the ring gear member244.

[0089] The planetary gear arrangement 218 also includes four torquetransmitting mechanisms 250, 252, 254 and 256. The torque-transmittingmechanisms 250, 252, 254 and 256 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0090] The input shaft 17 is continuously connected with the sun gearmember 242, and the output shaft 19 is continuously connected with thesun gear member 232. The ring gear member 224 is continuously connectedwith the planet carrier assembly member 236 through the interconnectingmember 270. The ring gear member 234 is continuously connected with theplanet carrier assembly member 246 through the interconnecting member272. The sun gear member 222 is continuously connected with thetransmission housing 260.

[0091] The planet carrier assembly member 226 is selectively connectablewith the sun gear member 232 through the clutch 250. The planet carrierassembly member 226 is selectively connectable with the ring gear member244 through the clutch 252. The planet carrier assembly member 236 isselectively connectable with the sun gear member 242 through the clutch254. The planet carrier assembly member 236 is selectively connectablewith the ring gear member 244 through the clutch 256.

[0092] As shown in the truth table in FIG. 3b, the torque transmittingmechanisms are engaged in combinations of two to establish five forwardspeed ratios and one reverse ratio. It should be also noted that thetorque transmitting mechanism 252 can remain engaged through the neutralcondition, thereby simplifying the forward/reverse interchange.

[0093] The reverse speed ratio is established with the engagement of theclutches 252 and 256. The clutch 252 connects the planet carrierassembly member 226 to the ring gear member 244, and the clutch 256connects the planet carrier assembly member 236 to the ring gear member244. The sun gear member 222 does not rotate. The planet carrierassembly member 226 rotates at the same speed as the ring gear member244, the planet carrier assembly member 236, and the ring gear member224. The ring gear member 234 rotates at the same speed as the planetcarrier assembly member 246. The sun gear member 232 rotates at the samespeed as the output shaft 19. The planet carrier assembly member 236rotates at a speed determined by the speed of the ring gear member 234,the speed of the sun gear member 232, and the ring gear/sun gear toothratio of the planetary gear set 230. The sun gear member 242 rotates atthe same speed as the input shaft 17. The planet carrier assembly member246 rotates at a speed determined by the speed of the ring gear member244, the speed of the sun gear member 242, and the ring gear/sun geartooth ratio of the planetary gear set 240. The overall numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 230 and 240.

[0094] The first forward speed ratio is established with the engagementof the clutches 250 and 252. The clutch 250 connects the planet carrierassembly member 226 to the sun gear member 232. The clutch 252 connectsthe planet carrier assembly member 226 to the ring gear member 244. Thesun gear member 222 does not rotate. The ring gear member 224 rotates atthe same speed as the planet carrier assembly member 236. The planetcarrier assembly member 226 rotates at the same speed as the ring gearmember 244, the sun gear member 232, and the output shaft 19. The speedof the planet carrier assembly member 226 is determined from the speedof the ring gear member 224 and the ring gear/sun gear tooth ratio ofthe planetary gear set 220. The ring gear member 234 rotates at the samespeed as the planet carrier assembly member 246. The planet carrierassembly member 236 rotates at a speed determined by the speed of thering gear member 234, the speed of the sun gear member 232, and the ringgear/sun gear tooth ratio of the planetary gear set 230. The sun gearmember 242 rotates at the same speed as the input shaft 17. The planetcarrier assembly member 246 rotates at a speed determined by the speedof the ring gear member 244, the speed of the sun gear member 242, andthe ring gear/sun gear tooth ratio of the planetary gear set 240. Theoverall numerical value of the first forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets220, 230 and 240.

[0095] The second forward speed ratio is established with the engagementof the clutches 250 and 256. The clutch 250 connects the planet carrierassembly member 226 to the sun gear member 232. The clutch 256 connectsthe planet carrier assembly member 236 to the ring gear member 244. Thesun gear member 222 does not rotate. The ring gear member 224 rotates atthe same speed as the planet carrier assembly member 236 and the ringgear member 244. The planet carrier assembly member 226 rotates at thesame speed as the sun gear member 232 and the output shaft 19. Theplanet carrier assembly member 226 rotates at a speed determined by thespeed of the ring gear member 224 and the ring gear/sun gear tooth ratioof the planetary gear set 220. The ring gear member 234 rotates at thesame speed as the planet carrier assembly member 246. The planet carrierassembly member 236 rotates at a speed determined by the speed of thering gear member 234, the speed of the sun gear member 232, and the ringgear/sun gear tooth ratio of the planetary gear set 230. The sun gearmember 242 rotates at the same speed as the input shaft 17. The planetcarrier assembly member 246 rotates at a speed determined by the speedof the ring gear member 244, the speed of the sun gear member 242, andthe ring gear/sun gear tooth ratio of the planetary gear set 240. Theoverall numerical value of the second forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets220, 230 and 240.

[0096] The third forward speed ratio is established with the engagementof the clutches 250 and 254. The clutch 250 connects the planet carrierassembly member 226 to the sun gear member 232. The clutch 254 connectsthe planet carrier assembly member 236 to the sun gear member 242. Thesun gear member 222 does not rotate. The ring gear member 224 rotates atthe same speed as the planet carrier assembly member 236, the sun gearmember 242, and the input shaft 17. The planet carrier assembly member226 rotates at the same speed as the sun gear member 232 and the outputshaft 19. The planet carrier assembly member 226 rotates at a speeddetermined by the speed of the ring gear member 224 and the ringgear/sun gear tooth ratio of the planetary gear set 220. The overallnumerical value of the third forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 220.

[0097] The fourth forward speed ratio is established with the engagementof the clutches 254 and 256. In this configuration, the input shaft 16is directly connected to the output shaft 19. The numerical value of thefourth forward speed ratio is 1.

[0098] The fifth forward speed ratio is established with the engagementof the clutches 252 and 254. The clutch 252 connects the planet carrierassembly member 226 to the ring gear member 244. The clutch 254 connectsthe planet carrier assembly member 236 to the sun gear member 242. Thesun gear member 222 does not rotate. The ring gear member 224 rotates atthe same speed as the planet carrier assembly member 236, the sun gearmember 242, and the input shaft 17. The planet carrier assembly member226 rotates at the same speed as the ring gear member 244. The planetcarrier assembly member 226 rotates at a speed determined by the speedof the ring gear member 224 and the ring gear/sun gear tooth ratio ofthe planetary gear set 220. The ring gear member 234 rotates at the samespeed as the planet carrier assembly member 246. The sun gear member 232rotates at the same speed as the output shaft 19. The planet carrierassembly member 236 rotates at a speed determined by the speed of thering gear member 234, the speed of the sun gear member 232, and the ringgear/sun gear tooth ratio of the planetary gear set 230. The planetcarrier assembly member 246 rotates at a speed determined by the speedof the ring gear member 244, the speed of the sun gear member 242, andthe ring gear/sun gear tooth ratio of the planetary gear set 240. Theoverall numerical value of the fifth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets220, 230 and 240.

[0099] As previously set forth, the truth table of FIG. 3b describes thecombinations of engagements utilized for the five forward speed ratiosand reverse ratio. The truth table also provides an example of speedratios that are available with the family member described above. Theseexamples of speed ratios are determined utilizing the tooth ratios givenin FIG. 3b. The R1/S1 value is the tooth ratio of the planetary gear set220; the R2/S2 value is the tooth ratio of the planetary gear set 230;and the R3/S3 value is the tooth ratio of the planetary gear set 240.Also depicted in FIG. 3b is a chart representing the ratio steps betweenadjacent forward speed ratios and the reverse to first forward speedratio. For example, the first to second ratio interchange has a step of1.59. It can also be readily determined from the truth table of FIG. 3bthat all of the single step forward ratio interchanges are of the singletransition variety, as are all of the double step forward interchanges.

[0100] A powertrain 310, shown in FIG. 4a, includes the engine andtorque converter 12, a planetary transmission 314, and the final drivemechanism 16. The planetary transmission 314 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 318, and output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 318 includes three planetary gear sets 320, 330 and 340.

[0101] The planetary gear set 320 includes a sun gear member 322, a ringgear member 324, and a planet carrier assembly member 326. The planetcarrier assembly member 326 includes a plurality of pinion gears 327rotatably mounted on a carrier member 329 and disposed in meshingrelationship with both the sun gear member 322 and the ring gear member324.

[0102] The planetary gear set 330 includes a sun gear member 332, a ringgear member 334, and a planet carrier assembly member 336. The planetcarrier assembly member 336 includes a plurality of pinion gears 337rotatably mounted on a carrier member 339 and disposed in meshingrelationship with both the sun gear member 332 and the ring gear member334.

[0103] The planetary gear set 340 includes a sun gear member 342, a ringgear member 344, and a planet carrier assembly member 346. The planetcarrier assembly member 346 includes a plurality of pinion gears 347rotatably mounted on a carrier member 349 and disposed in meshingrelationship with both the sun gear member 342 and the ring gear member344.

[0104] The planetary gear arrangement 318 also includes four torquetransmitting mechanisms 350, 352, 354 and 356. The torque-transmittingmechanisms 350, 352, 354 and 356 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0105] The input shaft 17 is continuously connected with the sun gearmember 342, and the output shaft 19 is continuously connected with thering gear member 344. The planet carrier assembly member 326 iscontinuously connected with the ring gear member 334 through theinterconnecting member 370. The sun gear member 332 is continuouslyconnected with the planet carrier assembly member 346 through theinterconnecting member 372. The sun gear member 322 is continuouslyconnected with the transmission housing 360.

[0106] The ring gear member 324 is selectively connectable with the sungear member 332 through the clutch 350. The ring gear member 324 isselectively connectable with the planet carrier assembly member 336through the clutch 352. The ring gear member 324 is selectivelyconnectable with the sun gear member 342 through the clutch 354. Thering gear member 334 is selectively connectable with the ring gearmember 344 through the clutch 356.

[0107] The truth tables given in FIGS. 4b, 5 b, 6 b, 7 b, 8 b, 9 b, 10b, 11 b, 12 b, 13 b, 14 b, 15 b and 16 b show the engagement sequencesfor the torque transmitting mechanisms to provide at least five forwardspeed ratios and one reverse ratio. As shown and described for theconfigurations in FIGS. 1a, 2 a and 3 a, those skilled in the art willunderstand from the respective truth tables how the speed ratios areestablished through the planetary gear sets identified in the writtendescription.

[0108] The truth table shown in FIG. 4b describes the engagementcombination and the engagement sequence necessary to provide the reversedrive ratio and the five forward speed ratios. A sample of the numericalvalues for the ratios is also provided in the truth table of FIG. 4b.These values are determined utilizing the ring gear/sun gear toothratios also given in FIG. 4b. The R1/S1 value is the tooth ratio for theplanetary gear set 320; the R2/S2 value is the tooth ratio for theplanetary gear set 330; and the R3/S3 value is the tooth ratio for theplanetary gear set 340. Also given in FIG. 4b is a chart describing thestep ratios between the adjacent forward speed ratios and the reverse tofirst forward speed ratio. For example, the first to second forwardspeed ratio step is 1.84. It can be readily determined from the truthtable of FIG. 4b that each of the forward single step ratio interchangesis a single transition shift, as are the double step interchanges. Thechart also shows that the torque transmitting mechanism 352 can beengaged through the neutral condition to simplify the forward/reverseinterchange.

[0109] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 340. The numerical values ofthe first and fifth forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 320, 330 and340. The numerical value of the second forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets320 and 340. The numerical value of the third forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 320. The numerical value of the fourth forward speed ratio is Apowertrain 410, shown in FIG. 5a, includes the engine and torqueconverter 12, a planetary transmission 414 and the final drive mechanism16. The planetary transmission 414 includes a planetary gear arrangement418, input shaft 17 and output shaft 19. The planetary gear arrangement418 includes three simple planetary gear sets 420, 430 and 440.

[0110] The planetary gear set 420 includes a sun gear member 422, a ringgear member 424, and a planet carrier assembly 426. The planet carrierassembly 426 includes a plurality of pinion gears 427 rotatably mountedon a carrier member 429 and disposed in meshing relationship with boththe sun gear member 422 and the ring gear member 424.

[0111] The planetary gear set 430 includes a sun gear member 432, a ringgear member 434, and a planet carrier assembly member 436. The planetcarrier assembly member 436 includes a plurality of pinion gears 437rotatably mounted on a carrier member 439 and disposed in meshingrelationship with both the sun gear member 432 and the ring gear member434.

[0112] The planetary gear set 440 includes a sun gear member 442, a ringgear member 444, and a planet carrier assembly member 446. The planetcarrier assembly member 446 includes a plurality of pinion gears 447rotatably mounted on a carrier member 449 and disposed in meshingrelationship with both the sun gear member 442 and the ring gear member444.

[0113] The planetary gear arrangement 418 also includes four torquetransmitting mechanisms 450, 452, 454 and 456. The torque transmittingmechanisms 450, 452, 454 and 458 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0114] The input shaft 17 is continuously connected with the sun gearmember 442, and the output shaft 19 is continuously connected with thering gear member 444. The planet carrier assembly member 426 iscontinuously connected with the ring gear member 434 through theinterconnecting member 470. The planet carrier assembly member 436 iscontinuously connected with the planet carrier assembly member 446through the interconnecting member 472. The sun gear member 422 iscontinuously connected with the transmission housing 460.

[0115] The ring gear member 424 is selectively connectable with theplanet carrier assembly member 436 through the clutch 450. The ring gearmember 424 is selectively connectable with the sun gear member 432through the clutch 452. The planet carrier assembly member 426 isselectively connectable with the sun gear member 442 through the clutch454. The ring gear member 434 is selectively connectable with the ringgear member 444 through the clutch 456.

[0116] The truth table shown in FIG. 5b describes the engagementcombination and sequence of the torque transmitting mechanisms 450, 452,454 and 456 that are employed to provide the reverse drive ratio and thefive forward speed ratios. It should be noted that the torquetransmitting mechanism 450 is engaged through the neutral condition tosimplify the forward/reverse interchange.

[0117] Also given in the truth table of FIG. 5b is a set of numericalvalues that are attainable with the present invention utilizing the ringgear/sun gear tooth ratios shown. The R1/S1 value is the tooth ratio ofthe planetary gear set 420; the R2/S2 value is the tooth ratio of theplanetary gear set 430; and the R3/S3 value is the tooth ratio of theplanetary gear set 440. As can also be determined from the truth tableof FIG. 5b, the single step forward interchanges are single transitionshifts, as are the double step interchanges in the forward direction.

[0118]FIG. 5b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse and first forward speed ratio.For example, the ratio step between the first and second forward speedratios is 1.63.

[0119] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 440. The numerical values ofthe first and fifth forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 420 and 440.The numerical values of the second and fourth forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 420, 430 and 440. The numerical value of the thirdforward speed ratio is 1.

[0120] A powertrain 510, shown in FIG. 6a, includes an engine and torqueconverter 12, a planetary gear transmission 514 and the final drivemechanism 16. The planetary transmission 514 includes the input shaft17, a planetary gear arrangement 518 and the output shaft 19. Theplanetary gear arrangement 518 includes three planetary gear sets 520,530 and 540.

[0121] The planetary gear set 520 includes a sun gear member 522, a ringgear member 524, and a planet carrier assembly 526. The planet carrierassembly 526 includes a plurality of pinion gears 527 rotatably mountedon a carrier member 529 and disposed in meshing relationship with boththe sun gear member 522 and the ring gear member 524.

[0122] The planetary gear set 530 includes a sun gear member 532, a ringgear member 534, and a planet carrier assembly member 536. The planetcarrier assembly member 536 includes a plurality of pinion gears 537rotatably mounted on a carrier member 539 and disposed in meshingrelationship with both the sun gear member 532 and the ring gear member534.

[0123] The planetary gear set 540 includes a sun gear member 542, a ringgear member 544, and a planet carrier assembly member 546. The planetcarrier assembly member 546 includes a plurality of pinion gears 547rotatably mounted on a carrier member 549 and disposed in meshingrelationship with both the sun gear member 542 and the ring gear member544.

[0124] The planetary gear arrangement 518 also includes four torquetransmitting mechanisms 550, 552, 554 and 556. The torque-transmittingmechanisms 550, 552, 554 and 556 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0125] The input shaft 17 is continuously connected with the sun gearmember 542, and the output shaft 19 is continuously connected with theplanet carrier assembly member 546. The ring gear member 524 iscontinuously connected with the planet carrier assembly member 536through the interconnecting member 570. The sun gear member 532 iscontinuously connected with the ring gear member 544 through theinterconnecting member 572. The sun gear member 522 is continuouslyconnected with the transmission housing 560.

[0126] The planet carrier assembly member 526 is selectively connectablewith the sun gear member 532 through the clutch 550. The planet carrierassembly member 526 is selectively connectable with the ring gear member534 through the clutch 552. The planet carrier assembly member 526 isselectively connectable with the sun gear member 542 through the clutch554. The ring gear member 534 is selectively connectable with the planetcarrier assembly member 546 through the clutch 556.

[0127] The truth table shown in FIG. 6b describes the engagementsequence and combination of the torque transmitting mechanisms toprovide the reverse speed ratio and five forward speed ratios. It shouldbe noted that the torque transmitting mechanism 552 can remain engagedthrough the neutral condition, thereby simplifying the forward/reverseinterchange. It can also be determined from the truth table of FIG. 6bthat all of the single step forward ratio interchanges are of the singletransition variety, as are all of the double step forward interchanges.The chart of FIG. 6b describes the ratio steps between adjacent forwardspeed ratios and the ratio step between the reverse and first forwardspeed ratio.

[0128] Those skilled in the art, upon reviewing the truth table and theschematic representation of FIG. 6a, can determine that the overallnumerical values of the reverse, second, fourth and fifth forward speedratios are determined utilizing the ring gear/sun gear tooth ratios ofthe planetary gear sets 520, 530 and 540. The numerical value of thefirst forward speed ratio is determined utilizing the ring gear/sun geartooth ratio of the planetary gear set 540. The numerical value of thethird forward speed ratio is 1.

[0129] The sample speed ratios given in the truth table are determinedutilizing the tooth ratio values also given in FIG. 6b. The R1/S1 valueis the tooth ratio of the planetary gear set 520; the R2/S2 value is thetooth ratio of the planetary gear set 530; and the R3/S3 value is thetooth ratio of the planetary gear set 540.

[0130] A powertrain 610, shown in FIG. 7a, has the engine and torqueconverter 12, a planetary transmission 614 and the final drive mechanism16. The planetary transmission 614 includes the input shaft 17, aplanetary gear arrangement 618 and the output shaft 19. The planetarygear arrangement 618 includes three planetary gear sets 620, 630 and640.

[0131] The planetary gear set 620 includes a sun gear member 622, a ringgear member 624, and a planet carrier assembly 626. The planet carrierassembly 626 includes a plurality of pinion gears 627 rotatably mountedon a carrier member 629 and disposed in meshing relationship with boththe sun gear member 622 and the ring gear member 624.

[0132] The planetary gear set 630 includes a sun gear member 632, a ringgear member 634, and a planet carrier assembly member 636. The planetcarrier assembly member 636 includes a plurality of pinion gears 637rotatably mounted on a carrier member 639 and disposed in meshingrelationship with both the sun gear member 632 and the ring gear member634.

[0133] The planetary gear set 640 includes a sun gear member 642, a ringgear member 644, and a planet carrier assembly member 646. The planetcarrier assembly member 646 includes a plurality of pinion gears 647rotatably mounted on a carrier member 649 and disposed in meshingrelationship with both the sun gear member 642 and the ring gear member644.

[0134] The planetary gear arrangement 618 also includes four torquetransmitting mechanisms 650, 652, 654 and 656. The torque-transmittingmechanisms 650, 652, 654 and 656 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0135] The input shaft 17 is continuously connected with the sun gearmember 642, and the output shaft 19 is continuously connected with thering gear member 644. The planet carrier assembly member 626 iscontinuously connected with the sun gear member 632 through theinterconnecting member 670. The ring gear member 634 is continuouslyconnected with the planet carrier assembly member 646 through theinterconnecting member 672. The sun gear member 622 is continuouslyconnected with the transmission housing 660.

[0136] The planet carrier assembly member 626 is selectively connectablewith the ring gear member 624 through the clutch 650. The ring gearmember 624 is selectively connectable with the planet carrier assemblymember 636 through the clutch 652. The planet carrier assembly member636 is selectively connectable with the sun gear member 642 through theclutch 654. The planet carrier assembly member 636 is selectivelyconnectable with the ring gear member 644 through the clutch 656.

[0137] The truth table shown in FIG. 7b describes the combination oftorque transmitting mechanism engagements that will provide the reversedrive ratio and the five forward speed ratios, as well as the sequenceof these engagements and interchanges. The torque transmitting mechanism650 can be engaged through the neutral condition, thereby simplifyingthe forward/reverse interchange. It can be noted from the truth tablethat each of the single step forward interchanges are single transitionratio changes, and the double step forward interchanges are also singletransition ratio changes.

[0138] The ratio values given are by way of example and are establishedutilizing the ring gear/sun gear tooth ratios given in FIG. 7b. Forexample, the R1/S1 value is the tooth ratio of the planetary gear set620; the R2/S2 value is the tooth ratio of the planetary gear set 630;and the R3/S3 value is the tooth ratio of the planetary gear set 640.The ratio steps between adjacent forward ratios and the reverse to firstforward speed ratio are also given in FIG. 7b.

[0139] Those skilled in the art will, upon reviewing the truth table ofFIG. 7b, recognize that the numerical value of the reverse speed ratiois determined utilizing the ring gear/sun gear tooth ratio of theplanetary gear set 640. The numerical values of the first and fifthforward speed ratios are determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 630 and 640. The numericalvalues of the second and fourth forward speed ratios are determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets620, 630 and 640. The numerical value of the third forward speed ratiois 1.

[0140] A powertrain 710, shown in FIG. 8a, has the conventional engineand torque converter 12, a planetary transmission 714, and theconventional final drive mechanism 16. The engine and torque converter12 are drivingly connected with the planetary transmission 714 throughthe input shaft 17. The planetary transmission 714 is drivinglyconnected with the final drive mechanism 16 through the output shaft 19.The planetary transmission 714 includes a planetary gear arrangement 718that has a first planetary gear set 720, a second planetary gear set730, and a third planetary gear set 740.

[0141] The planetary gear set 720 includes a sun gear member 722, a ringgear member 724, and a planet carrier assembly 726. The planet carrierassembly 726 includes a plurality of pinion gears 727 rotatably mountedon a carrier member 729 and disposed in meshing relationship with boththe sun gear member 722 and the ring gear member 724.

[0142] The planetary gear set 730 includes a sun gear member 732, a ringgear member 734, and a planet carrier assembly member 736. The planetcarrier assembly member 736 includes a plurality of pinion gears 737rotatably mounted on a carrier member 739 and disposed in meshingrelationship with both the sun gear member 732 and the ring gear member734.

[0143] The planetary gear set 740 includes a sun gear member 742, a ringgear member 744, and a planet carrier assembly member 746. The planetcarrier assembly member 7 46 includes a plurality of pinion gears 7 47rotatably mounted on a carrier member 749 and disposed in meshingrelationship with both the sun gear member 742 and the ring gear member744.

[0144] The planetary gear arrangement 718 also includes four torquetransmitting mechanisms 750, 752, 754 and 756. The torque transmittingmechanisms 750, 752, 754 and 756 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0145] The input shaft 17 is continuously connected with the sun gearmember 742, and the output shaft 19 is continuously connected with thering gear member 744. The ring gear member 724 is continuously connectedwith the sun gear member 732 through the interconnecting member 770. Theplanet carrier assembly member 736 is continuously connected with theplanet carrier assembly member 746 through the interconnecting member772. The sun gear member 722 is continuously connected with thetransmission housing 760.

[0146] The planet carrier assembly member 726 is selectively connectablewith the ring gear member 734 through the clutch 750. The planet carrierassembly member 726 is selectively connectable with the sun gear member742 through the clutch 752. The planet carrier assembly member 726 isselectively connectable with the ring gear member 744 through the clutch754. The planet carrier assembly member 736 is selectively connectablewith the ring gear member 734 through the clutch 756.

[0147] The truth table of FIG. 8b defines the torque transmittingmechanism engagement sequence utilized for each of the forward speedratios and the reverse speed ratio. Also given in the truth table is aset of numerical values that are attainable with the present inventionutilizing the ring gear/sun gear tooth ratios given in FIG. 8b. TheR1/S1 value is the tooth ratio of the planetary gear set 720; the R2/S2value is the tooth ratio of the planetary gear set 730; and the R3/S3value is the tooth ratio of the planetary gear set 740. As can also bedetermined from the truth table of FIG. 8b, the single step forwardinterchanges are single transition shifts, as are the double stepinterchanges in the forward direction.

[0148]FIG. 8b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse and first forward ratio. Forexample, the ratio step between the first and second forward ratios is1.74. Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 740. The numerical values ofthe first and fifth forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 720 and 740.The numerical values of the second and fourth forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 720, 730 and 740. The numerical value of the thirdforward speed ratio is 1.

[0149] A powertrain 810, shown in FIG. 9a, has the conventional engineand torque converter 12, a planetary transmission 814, and the finaldrive mechanism 16. The engine and torque converter 12 are drivinglyconnected with the planetary transmission 814 through the input shaft17. The planetary transmission 814 is drivingly connected with the finaldrive mechanism 16 through the output shaft 19. The planetarytransmission 814 includes a planetary gear arrangement 818 that has afirst planetary gear set 820, a second planetary gear set 830, and athird planetary gear set 840.

[0150] The planetary gear set 820 includes a sun gear member 822, a ringgear member 824, and a planet carrier assembly 826. The planet carrierassembly 826 includes a plurality of pinion gears 827 rotatably mountedon a carrier member 829 and disposed in meshing relationship with boththe sun gear member 822 and the ring gear member 824.

[0151] The planetary gear set 830 includes a sun gear member 832, a ringgear member 834, and a planet carrier assembly member 836. The planetcarrier assembly member 836 includes a plurality of pinion gears 837rotatably mounted on a carrier member 839 and disposed in meshingrelationship with both the sun gear member 832 and the ring gear member834.

[0152] The planetary gear set 840 includes a sun gear member 842, a ringgear member 844, and a planet carrier assembly member 846. The planetcarrier assembly member 846 includes a plurality of pinion gears 847rotatably mounted on a carrier member 849 and disposed in meshingrelationship with both the sun gear member 842 and the ring gear member844.

[0153] The planetary gear arrangement 818 also includes four torquetransmitting mechanisms 850, 852, 854 and 856. The torque-transmittingmechanisms 850, 852, 854 and 856 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0154] The input shaft 17 is continuously connected with the sun gearmember 842, and the output shaft 19 is continuously connected with thering gear member 834. The sun gear member 822 is continuously connectedwith the sun gear member 832 through the interconnecting member 870. Theplanet carrier assembly member 836 is continuously connected with thering gear member 844 through the interconnecting member 872. The planetcarrier assembly member 826 is continuously connected with thetransmission housing 860.

[0155] The sun gear member 822 is selectively connectable with the ringgear member 824 through the clutch 850. The planet carrier assemblymember 846 is selectively connectable with the ring gear member 824through the clutch 852. The ring gear member 834 is selectivelyconnectable with the planet carrier assembly member 846 through theclutch 854. The planet carrier assembly member 846 is selectivelyconnectable with the sun gear member 842 through the clutch 856.

[0156] The truth table shown in FIG. 9b defines the torque transmittingmechanism engagement sequence that provides the reverse ratio and fiveforward speed ratios shown in the truth table and available with theplanetary gear arrangement 818. The truth table indicates that thetorque transmitting mechanism 852 can remain engaged through the neutralcondition, thereby simplifying the forward/reverse interchange. A sampleof numerical values for the individual ratios is also given in the truthtable of FIG. 9b. These numerical values have been calculated utilizingthe ring gear/sun gear tooth ratios also given by way of example in FIG.9b. The R1/S1 value is the tooth ratio of the planetary gear set 820;the R2/S2 value is the tooth ratio of the planetary gear set 830; andthe R3/S3 value is the tooth ratio of the planetary gear set 840. It canbe readily recognized from the truth table that all of the single anddouble step forward interchanges are single transition ratiointerchanges. FIG. 9b also describes the ratio steps between adjacentforward ratios and between the reverse and first forward speed ratio.For example, the ratio step between the first and second forward ratiosis 1.64.

[0157] Those skilled in the art of planetary transmissions willrecognize that the numerical values of the reverse and second forwardspeed ratios are determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 830 and 840. The numerical value ofthe first forward speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 820, 830 and 840. Thenumerical value of the third forward speed ratio is 1. The numericalvalue of the fourth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 830. The numericalvalue of the fifth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 820 and 830.

[0158] The powertrain 910, shown in FIG. 10a, includes the conventionalengine and torque converter 12, a planetary transmission 914, and theconventional final drive mechanism 16. The engine and torque converter12 are drivingly connected with the planetary transmission 914 throughthe input shaft 17. The planetary transmission 914 is drivinglyconnected with the final drive mechanism 16 through the output shaft 19.The planetary transmission 914 includes a planetary gear arrangement 918that has a first planetary gear set 920, a second planetary gear set930, and a third planetary gear set 940.

[0159] The planetary gear set 920 includes a sun gear member 922, a ringgear member 924, and a planet carrier assembly 926. The planet carrierassembly 926 includes a plurality of intermeshing pinion gears 927 thatare rotatably mounted on a carrier member 929 and disposed in meshingrelationship with the sun gear member 922 and the ring gear member 924,respectively.

[0160] The planetary gear set 930 includes a sun gear member 932, a ringgear member 934, and a planet carrier assembly member 936. The planetcarrier assembly member 936 includes a plurality of pinion gears 937rotatably mounted on a carrier member 939 and disposed in meshingrelationship with both the sun gear member 932 and the ring gear member934.

[0161] The planetary gear set 940 includes a sun gear member 942, a ringgear member 944, and a planet carrier assembly member 946. The planetcarrier assembly member 946 includes a plurality of pinion gears 947rotatably mounted on a carrier member 949 and disposed in meshingrelationship with both the sun gear member 942 and the ring gear member944.

[0162] The planetary gear arrangement 918 also includes four torquetransmitting mechanisms 950, 952, 954 and 956. The torque transmittingmechanisms 950, 952, 954 and 956 are rotating type torque transmittingmechanisms, commonly termed clutches.

[0163] The input shaft 17 is continuously connected with the ring gearmember 944, and the output shaft 19 is continuously connected with theplanet carrier assembly member 946. The sun gear member 922 iscontinuously connected with the sun gear member 932 through theinterconnecting member 970. The ring gear member 934 is continuouslyconnected with the planet carrier assembly member 946 through theinterconnecting member 972. The ring gear member 924 is continuouslyconnected with the transmission housing 960.

[0164] The planet carrier assembly member 926 is selectively connectablewith the planet carrier assembly member 936 through the clutch 950. Theplanet carrier assembly member 926 is selectively connectable with thesun gear member 942 through the clutch 952. The planet carrier assemblymember 926 is selectively connectable with the ring gear member 944through the clutch 954. The sun gear member 932 is selectivelyconnectable with the sun gear member 942 through the clutch 956.

[0165] The truth table of FIG. 10b describes the torque transmittingmechanism engagement sequence utilized to provide the reverse speedratio and five forward speed ratios. The truth table also provides a setof examples for the ratios for each of the reverse and forward speedratios. These numerical values have been determined utilizing the ringgear/sun gear tooth ratios given in FIG. 10b. The R1/S1 value is thetooth ratio of the planetary gear set 920; the R2/S2 value is the toothratio of the planetary gear set 930; and the R3/S3 value is the toothratio of the planetary gear set 940. It can also be determined from thetruth table of FIG. 10b that each of the forward single step and doublestep ratio interchanges are of the single transition variety.

[0166] Those skilled in the art, upon reviewing the engagementcombinations, will recognize that the numerical value of the reversespeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 920 and 930. The numerical values of thefirst and second forward speed ratios are determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 920, 930 and 940.The numerical value of the third forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratio of the planetary gear set940. The numerical value of the fourth forward speed ratio is 1. Thenumerical value of the fifth forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 920 and940.

[0167] A powertrain 1010, shown in FIG. 11a, includes the conventionalengine and torque converter 12, a planetary transmission 1014, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1014 through theinput shaft 17. The planetary transmission 1014 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1014 includes a planetary gear arrangement 1018that has a first planetary gear set 1020, a second planetary gear set1030, and a third planetary gear set 1040.

[0168] The planetary gear set 1020 includes a sun gear member 1022, aring gear member 1024, and a planet carrier assembly 1026. The planetcarrier assembly 1026 includes a plurality of pinion gears 1027rotatably mounted on a carrier member 1029 and disposed in meshingrelationship with both the sun gear member 1022 and the ring gear member1024.

[0169] The planetary gear set 1030 includes a sun gear member 1032, aring gear member 1034, and a planet carrier assembly member 1036. Theplanet carrier assembly member 1036 includes a plurality of pinion gears1037 rotatably mounted on a carrier member 1039 and disposed in meshingrelationship with both the sun gear member 1032 and the ring gear member1034.

[0170] The planetary gear set 1040 includes a sun gear member 1042, aring gear member 1044, and a planet carrier assembly member 1046. Theplanet carrier assembly member 1046 includes a plurality of pinion gears1047 rotatably mounted on a carrier member 1049 and disposed in meshingrelationship with both the sun gear member 1042 and the ring gear member1044.

[0171] The planetary gear arrangement 1018 also includes four torquetransmitting mechanisms 1050, 1052, 1054 and 1056. Thetorque-transmitting mechanisms 1050, 1052, 1054 and 1056 are rotatingtype torque transmitting mechanisms, commonly termed clutches.

[0172] The input shaft 17 is continuously connected with the ring gearmember 1044, and the output shaft 19 is continuously connected with theplanet carrier assembly member 1046. The ring gear member 1024 iscontinuously connected with the ring gear member 1034 through theinterconnecting member 1070. The sun gear member 1032 is continuouslyconnected with the sun gear member 1042 through the interconnectingmember 1072. The planet carrier assembly member 1026 is continuouslyconnected with the transmission housing 1060.

[0173] The sun gear member 1022 is selectively connectable with the sungear member 1032 through the clutch 1050. The sun gear member 1022 isselectively connectable with the planet carrier assembly member 1036through the clutch 1052. The sun gear member 1022 is selectivelyconnectable with the ring gear member 1044 through the clutch 1054. Thering gear member 1034 is selectively connectable with the planet carrierassembly member 1046 through the clutch 1056.

[0174] The truth table shown in FIG. 11b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the five forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 11b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 11b. The R1/S1 value is the tooth ratiofor the planetary gear set 1020; the R2/S2 value is the tooth ratio forthe planetary gear set 1030; and the R3/S3 value is the tooth ratio forthe planetary gear set 1040. Also given in FIG. 11b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0175] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 1020. The numerical values ofthe first and fifth forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 1020, 1030and 1040. The numerical value of the second forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1020 and 1040. The numerical value of the thirdforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1040. The numerical value of the fourthforward speed ratio is 1.

[0176] A powertrain 1110, shown in FIG. 12a, includes the conventionalengine and torque converter 12, a planetary transmission 1114, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1114 through theinput shaft 17. The planetary transmission 1114 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1114 includes a planetary gear arrangement 1118that has a first planetary gear set 1120, a second planetary gear set1130, and a third planetary gear set 1140.

[0177] The planetary gear set 1120 includes a sun gear member 1122, aring gear member 1124, and a planet carrier assembly 1126. The planetcarrier assembly 1126 includes a plurality of pinion gears 1127rotatably mounted on a carrier member 1129 and disposed in meshingrelationship with both the sun gear member 1122 and the ring gear member1124.

[0178] The planetary gear set 1130 includes a sun gear member 1132, aring gear member 1134, and a planet carrier assembly member 1136. Theplanet carrier assembly member 1136 includes a plurality of pinion gears1137 rotatably mounted on a carrier member 1139 and disposed in meshingrelationship with both the sun gear member 1132 and the ring gear member1134.

[0179] The planetary gear set 1140 includes a sun gear member 1142, aring gear member 1144, and a planet carrier assembly member 1146. Theplanet carrier assembly member 1146 includes a plurality of pinion gears1147 rotatably mounted on a carrier member 1149 and disposed in meshingrelationship with both the sun gear member 1142 and the ring gear member1144.

[0180] The planetary gear arrangement 1118 also includes four torquetransmitting mechanisms 1150, 1152, 1154 and 1156. The torquetransmitting mechanisms 1150, 1152, 1154 and 1156 are rotating typetorque transmitting mechanisms, commonly termed clutches.

[0181] The input shaft 17 is continuously connected with the sun gearmember 1142, and the output shaft 19 is continuously connected with thering gear member 1134. The ring gear member 1124 is continuouslyconnected with the planet carrier assembly member 1136 through theinterconnecting member 1170. The sun gear member 1132 is continuouslyconnected with the ring gear member 1144 through the interconnectingmember 1172. The sun gear member 1122 is continuously connected with thetransmission housing 1160.

[0182] The planet carrier assembly member 1126 is selectivelyconnectable with the ring gear member 1134 through the clutch 1150. Theplanet carrier assembly member 1146 is selectively connectable with theplanet carrier assembly member 1126 through the clutch 1152. The planetcarrier assembly member 1136 is selectively connectable with the sungear member 1142 through the clutch 1154. The sun gear member 1142 isselectively connectable with the planet carrier assembly member 1146through the clutch 1156.

[0183] The truth table shown in FIG. 12b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the five forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 12b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 12b. The R1/S1 value is the tooth ratiofor the planetary gear set 1120; the R2/S2 value is the tooth ratio forthe planetary gear set 1130; and the R3/S3 value is the tooth ratio forthe planetary gear set 1140. Also given in FIG. 12b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0184] Those skilled in the art will recognize that the numerical valuesof the reverse and fourth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1120,1130 and 1140. The numerical values of the first and fifth forward speedratios are determined utilizing the ring gear/sun gear tooth ratios ofthe planetary gear sets 1120 and 1130. The numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1120. The numerical value of the thirdforward speed ratio is 1.

[0185] A powertrain 1210, shown in FIG. 13a, includes the conventionalengine and torque converter 12, a planetary transmission 1214, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1214 through theinput shaft 17. The planetary transmission 1214 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1214 includes a planetary gear arrangement 1218that has a first planetary gear set 1220, a second planetary gear set1230, and a third planetary gear set 1240.

[0186] The planetary gear set 1220 includes a sun gear member 1222, aring gear member 1224, and a planet carrier assembly 1226. The planetcarrier assembly 1226 includes a plurality of pinion gears 1227 and 1228rotatably mounted on a carrier member 1229 and disposed in meshingrelationship with both the sun gear member 1222 and the ring gear member1224.

[0187] The planetary gear set 1230 includes a sun gear member 1232, aring gear member 1234, and a planet carrier assembly member 1236. Theplanet carrier assembly member 1236 includes a plurality of pinion gears1237 rotatably mounted on a carrier member 1239 and disposed in meshingrelationship with both the sun gear member 1232 and the ring gear member1234.

[0188] The planetary gear set 1240 includes a sun gear member 1242, aring gear member 1244, and a planet carrier assembly member 1246. Theplanet carrier assembly member 1246 includes a plurality of pinion gears1247 rotatably mounted on a carrier member 1249 and disposed in meshingrelationship with both the sun gear member 1242 and the ring gear member1244.

[0189] The planetary gear arrangement 1218 also includes four torquetransmitting mechanisms 1250, 1252, 1254 and 1256. The torquetransmitting mechanisms 1250, 1252, 1254 and 1256 are rotating typetorque transmitting mechanisms, commonly termed clutches.

[0190] The input shaft 17 is continuously connected with the sun gearmember 1232, and the output shaft 19 is continuously connected with theplanet carrier assembly member 1236. The sun gear member 1222 iscontinuously connected with the ring gear member 1234 through theinterconnecting member 1270. The planet carrier assembly member 1236 iscontinuously connected with the sun gear member 1242 through theinterconnecting member 1272. The planet carrier assembly member 1226 iscontinuously connected with the transmission housing 1260.

[0191] The planet carrier assembly member 1246 is selectivelyconnectable with the ring gear member 1224 through the clutch 1250. Thering gear member 1224 is selectively connectable with the ring gearmember 1244 through the clutch 1252. The ring gear member 1234 isselectively connectable with the planet carrier assembly member 1246through the clutch 1254. The planet carrier assembly member 1246 isselectively connectable with the sun gear member 1232 through the clutch1256.

[0192] The truth table shown in FIG. 13b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the five forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 13b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 13b. The R1/S1 value is the tooth ratiofor the planetary gear set 1220; the R2/S2 value is the tooth ratio forthe planetary gear set 1230; and the R3/S3 value is the tooth ratio forthe planetary gear set 1240. Also given in FIG. 13b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0193] Those skilled in the art will recognize that the numerical valuesof the reverse and fifth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1220 and1230. The numerical value of the first forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratio of the planetary gear set1230. The numerical values of the second and fourth forward speed ratiosare determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1220, 1230 and 1240. The numerical value of thethird forward speed ratio is 1.

[0194] A powertrain 1310, shown in FIG. 14a, includes the conventionalengine and torque converter 12, a planetary transmission 1314, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1314 through theinput shaft 17. The planetary transmission 1314 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1314 includes a planetary gear arrangement 1318that has a first planetary gear set 1320, a second planetary gear set1330, and a third planetary gear set 1340.

[0195] The planetary gear set 1320 includes a sun gear member 1322, aring gear member 1324, and a planet carrier assembly 1326. The planetcarrier assembly 1326 includes a plurality of pinion gears 1327rotatably mounted on a carrier member 1329 and disposed in meshingrelationship with both the sun gear member 1322 and the ring gear member1324.

[0196] The planetary gear set 1330 includes a sun gear member 1332, aring gear member 1334, and a planet carrier assembly member 1336. Theplanet carrier assembly member 1336 includes a plurality of pinion gears1337 rotatably mounted on a carrier member 1339 and disposed in meshingrelationship with both the sun gear member 1332 and the ring gear member1334.

[0197] The planetary gear set 1340 includes a sun gear member 1342, aring gear member 1344, and a planet carrier assembly member 1346. Theplanet carrier assembly member 1346 includes a plurality of pinion gears1347 rotatably mounted on a carrier member 1349 and disposed in meshingrelationship with both the sun gear member 1342 and the ring gear member1344.

[0198] The planetary gear arrangement 1318 also includes four torquetransmitting mechanisms 1350, 1352, 1354 and 1356. The torquetransmitting mechanisms 1350, 1352, 1354 and 1356 are rotating-typetorque transmitting mechanisms, commonly termed clutches.

[0199] The input shaft 17 is continuously connected with the sun gearmember 1332, and the output shaft 19 is continuously connected with thesun gear member 1342. The ring gear member 1324 is continuouslyconnected with the planet carrier assembly member 1336 through theinterconnecting member 1370. The ring gear member 1334 is continuouslyconnected with the ring gear member 1344 through the interconnectingmember 1372. The sun gear member 1322 is continuously connected with thetransmission housing 1360.

[0200] The planet carrier assembly member 1326 is selectivelyconnectable with the sun gear member 1332 through the clutch 1350. Theplanet carrier assembly member 1346 is selectively connectable with theplanet carrier assembly member 1326 through the clutch 1352. The planetcarrier assembly member 1336 is selectively connectable with the planetcarrier assembly member 1346 through the clutch 1354. The planet carrierassembly member 1346 is selectively connectable with the sun gear member1342 through the clutch 1356.

[0201] The truth table shown in FIG. 14b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the five forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 14b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 14b. The R1/S1 value is the tooth ratiofor the planetary gear set 1320; the R2/S2 value is the tooth ratio forthe planetary gear set 1330; and the R3/S3 value is the tooth ratio forthe planetary gear set 1340. Also given in FIG. 14b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0202] Those skilled in the art will recognize that the numerical valuesof the reverse and fourth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1320,1330 and 1340. The numerical values of the first and fifth forward speedratios are determined utilizing the ring gear/sun gear tooth ratios ofthe planetary gear sets 1320 and 1330. The numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1330 and 1340. The numerical value ofthe third forward speed ratio is 1.

[0203] A powertrain 1410, shown in FIG. 15a, includes the conventionalengine and torque converter 12, a planetary transmission 1414, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1414 through theinput shaft 17. The planetary transmission 1414 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1414 includes a planetary gear arrangement 1418that has a first planetary gear set 1420, a second planetary gear set1430, and a third planetary gear set 1440.

[0204] The planetary gear set 1420 includes a sun gear member 1422, aring gear member 1424, and a planet carrier assembly 1426. The planetcarrier assembly 1426 includes a plurality of pinion gears 1427rotatably mounted on a carrier member 1429 and disposed in meshingrelationship with both the sun gear member 1422 and the ring gear member1424.

[0205] The planetary gear set 1430 includes a sun gear member 1432, aring gear member 1434, and a planet carrier assembly member 1436. Theplanet carrier assembly member 1436 includes a plurality of pinion gears1437 rotatably mounted on a carrier member 1439 and disposed in meshingrelationship with both the sun gear member 1432 and the ring gear member1434.

[0206] The planetary gear set 1440 includes a sun gear member 1442, aring gear member 1444, and a planet carrier assembly member 1446. Theplanet carrier assembly member 1446 includes a plurality of pinion gears1447 rotatably mounted on a carrier member 1449 and disposed in meshingrelationship with both the sun gear member 1442 and the ring gear member1444.

[0207] The planetary gear arrangement 1418 also includes four torquetransmitting mechanisms 1450, 1452, 1454 and 1456. The torquetransmitting mechanisms 1450, 1452, 1454 and 1456 are rotating typetorque transmitting mechanisms, commonly termed clutches.

[0208] The input shaft 17 is continuously connected with the sun gearmember 1442, and the output shaft 19 is continuously connected with theplanet carrier assembly member 1436. The ring gear member 1424 iscontinuously connected with the sun gear member 1432 through theinterconnecting member 1470. The planet carrier assembly member 1436 iscontinuously connected with the ring gear member 1444 through theinterconnecting member 1472. The sun gear member 1422 is continuouslyconnected with the transmission housing 1460.

[0209] The planet carrier assembly member 1426 is selectivelyconnectable with the ring gear member 1424 through the clutch 1450. Theplanet carrier assembly member 1446 is selectively connectable with theplanet carrier assembly member 1426 through the clutch 1452. The ringgear member 1434 is selectively connectable with the sun gear member1442 through the clutch 1454. The ring gear member 1434 is selectivelyconnectable with the planet carrier assembly member 1446 through theclutch 1456.

[0210] The truth table shown in FIG. 15b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the five forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 15b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 15b. The R1/S1 value is the tooth ratiofor the planetary gear set 1420; the R2/S2 value is the tooth ratio forthe planetary gear set 1430; and the R3/S3 value is the tooth ratio forthe planetary gear set 1440. Also given in FIG. 15b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0211] One skilled in the art will recognize that the numerical value ofthe reverse speed ratio is determined utilizing the ring gear/sun geartooth ratio of the planetary gear set 1440. The numerical value of thefirst forward speed ratio is determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 1430 and 1440. The numericalvalue of the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 1430. The numericalvalue of the third forward speed ratio is 1. The numerical values of thefourth and fifth forward speed ratios are determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1420, 1430 and1440.

[0212] A powertrain 1510, shown in FIG. 16a, includes the conventionalengine and torque converter 12, a planetary transmission 1514, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1514 through theinput shaft 17. The planetary transmission 1514 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1514 includes a planetary gear arrangement 1518that has a first planetary gear set 1520, a second planetary gear set1530, and a third planetary gear set 1540.

[0213] The planetary gear set 1520 includes a sun gear member 1522, aring gear member 1524, and a planet carrier assembly 1526. The planetcarrier assembly 1526 includes a plurality of pinion gears 1527rotatably mounted on a carrier member 1529 and disposed in meshingrelationship with both the sun gear member 1522 and the ring gear member1524.

[0214] The planetary gear set 1530 includes a sun gear member 1532, aring gear member 1534, and a planet carrier assembly member 1536. Theplanet carrier assembly member 1536 includes a plurality of pinion gears1537 rotatably mounted on a carrier member 1539 and disposed in meshingrelationship with both the sun gear member 1532 and the ring gear member1534.

[0215] The planetary gear set 1540 includes a sun gear member 1542, aring gear member 1544, and a planet carrier assembly member 1546. Theplanet carrier assembly member 1546 includes a plurality of pinion gears1547 rotatably mounted on a carrier member 1549 and disposed in meshingrelationship with both the sun gear member 1542 and the ring gear member1544.

[0216] The planetary gear arrangement 1518 also includes four torquetransmitting mechanisms 1550, 1552, 1554 and 1556. The torquetransmitting mechanism 1550, 1552, 1554 and 1556 are rotating-typetorque transmitting mechanisms, commonly termed clutches.

[0217] The input shaft 17 is continuously connected with the sun gearmember 1542, and the output shaft 19 is continuously connected with thering gear member 1534. The ring gear member 1524 is continuouslyconnected with the planet carrier assembly member 1536 through theinterconnecting member 1570. The sun gear member 1532 is continuouslyconnected with the ring gear member 1544 through the interconnectingmember 1572. The sun gear member 1522 is continuously connected with thetransmission housing 1560.

[0218] The planet carrier assembly member 1526 is selectivelyconnectable with the ring gear member 1534 through the clutch 1550. Theplanet carrier assembly member 1526 is selectively connectable with theplanet carrier assembly member 1546 through the clutch 1552. The sungear member 1542 is selectively connectable with the planet carrierassembly member 1536 through the clutch 1554. The ring gear member 1544is selectively connectable with the planet carrier assembly member 1546through the clutch 1556.

[0219] The truth table shown in FIG. 16b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the five forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 16b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 16b. The R1/S1 value is the tooth ratiofor the planetary gear set 1520; the R2/S2 value is the tooth ratio forthe planetary gear set 1530; and the R3/S3 value is the tooth ratio forthe planetary gear set 1540. Also given in FIG. 16b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0220] One skilled in the art will recognize that the numerical valuesof the reverse and fourth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1520,1530 and 1540. The numerical values of the first and fifth forward speedratios are determined utilizing the ring gear/sun gear tooth ratios ofthe planetary gear sets 1520 and 1530. The numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1520. The numerical value of the thirdforward speed ratio is 1.

[0221] While the best modes for carrying out the invention have beendescribed in detail, those familiar with the art to which this inventionrelates will recognize various alternative designs and embodiments forpracticing the invention within the scope of the appended claims.

What is claimed is:
 1. A family of transmissions wherein each familymember comprises: an input shaft; an output shaft; first, second andthird planetary gear sets each having first, second and third members;said input shaft being continuously interconnected with a member of theplanetary gear sets, said output shaft being continuously interconnectedwith another member of the planetary gear sets; a first interconnectingmember continuously interconnecting said first member of said firstplanetary gear set with said first member of said second planetary gearset; a second interconnecting member continuously interconnecting saidsecond member of said second planetary gear set with said first memberof said third planetary gear set; a transmission housing continuouslyinterconnected with said second member of said first planetary gear set;a first clutch selectively interconnecting a member of said firstplanetary gear set with said input shaft, said output shaft, said firstor second interconnecting member or a member of said second or thirdplanetary gear sets; a second clutch selectively interconnecting amember of said second planetary gear set with said input shaft, saidoutput shaft, or a member of said first or third planetary gear sets; athird clutch selectively interconnecting a member of said thirdplanetary gear set with said input shaft, said output shaft, said firstor second interconnecting member, or a member of said first or secondplanetary gear set; a fourth clutch selectively interconnecting a memberof said first, second, or third planetary gear sets with another memberof said first, second, or third planetary gear sets; and said first,second, third or fourth clutches being engaged in combinations of two toestablish at least five forward speed ratios and a reverse speed ratiobetween said input shaft and said output shaft.
 2. The family oftransmissions in claim 1, wherein planet carrier assembly members ofeach of said planetary gear sets are of the single-pinion type.
 3. Thefamily of transmissions in claim 1, wherein a planet carrier assemblymember of at least one of said planetary carrier gear sets is of thedouble-pinion type.
 4. A family of transmissions having a plurality offamily members wherein each family member comprises: an input shaft; anoutput shaft; a planetary gear arrangement having first, second andthird planetary gear sets, each planetary gear set having first, secondand third members; said input shaft being continuously interconnectedwith a member of the planetary gear sets, said output shaft beingcontinuously interconnected with another member of the planetary gearsets; a first interconnecting member continuously interconnecting saidfirst member of said first planetary gear set with said first member ofsaid second planetary gear set; a second interconnecting membercontinuously interconnecting said second member of said second planetarygear set with said first member of said third planetary gear set; atransmission housing continuously interconnected with said second memberof said first planetary gear set; and four selectively engageableclutches for selectively interconnecting said members of said planetarygear sets with said input shaft, said output shaft, one of said first orsecond interconnecting members, or another member of one of saidplanetary gear sets, said clutches being engaged in combinations of twoto establish at least five forward speed ratios and one reverse speedratio between said input shaft and said output shaft.
 5. The family oftransmissions defined in claim 4, wherein a first of said four clutchesis selectively operable for interconnecting a member of said firstplanetary gear set with said input shaft, said output shaft, said firstor second interconnecting member or a member of said second or thirdplanetary gear sets.
 6. The family of transmissions defined in claim 4,wherein a second of said four clutches is selectively operable forinterconnecting a member of said second planetary gear set with saidinput shaft, said output shaft, or a member of said first or thirdplanetary gear sets.
 7. The family of transmissions defined in claim 4,wherein a third of said four clutches is selectively operable forinterconnecting a member of said third planetary gear set with saidinput shaft, said output shaft, said first or second interconnectingmember, or a member of said first or second planetary gear set.
 8. Thefamily of transmissions defined in claim 4, wherein a fourth of saidfour clutches is selectively operable for interconnecting a member ofsaid first, second, or third planetary gear sets with another member ofsaid first, second, or third planetary gear sets.
 9. The family oftransmissions in claim 4, wherein planet carrier assembly members ofeach of said planetary gear sets are of the single-pinion type.
 10. Thefamily of transmissions in claim 4, wherein a planet carrier assemblymember of at least one of said planetary carrier gear sets is of thedouble-pinion type.